Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch with lockup resistance member

ABSTRACT

A torque converter includes an impeller, a turbine-piston hydrodynamically drivable by the impeller, a stator, and an annular lockup resistance member. The impeller includes an impeller shell. The turbine-piston includes a turbine-piston shell. The turbine-piston shell includes a turbine-piston flange having a first flange surface facing an engagement surface of the impeller shell. The turbine-piston is movable axially toward and away from the engagement surface to position the torque converter into and out of a lockup mode in which the turbine-piston flange is mechanically locked to the impeller shell. The annular lockup resistance member is in the form of an annular elastomeric sandwich washer coaxially aligned with the rotational axis and including turbine-side and stator-side members, and an elastomeric inner member sandwiched between the turbine-side and stator-side members.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention generally relates to torque converters andhydrokinetic torque coupling devices, and more particularly to torqueconverters and hydrokinetic torque coupling devices includingturbine-piston lockup clutches for mechanically coupling driving anddriven shafts.

2. Description of the Related Art

Generally, vehicles with automatic transmissions are equipped with ahydrokinetic torque coupling device for fluidly coupling the drivingshaft of an engine to a driven shaft of a transmission. Lockup clutchesare known for mechanically coupling the driving and driven shafts undercertain operating conditions. Lockup clutches and their operation aredescribed in, for example, U.S. Pat. No. 8,276,723 and U.S. Pat. No.7,191,879.

While hydrokinetic torque coupling devices with lockup clutches haveproven to be useful for vehicular driveline applications and conditions,improvements that may enhance their performance and cost are possible.

As taught hereinbelow, such improvements may derive from, for example,reducing the spatial requirements of components of the hydrokinetictorque coupling device and/or consolidating functions of two or morecomponents into a single component.

BRIEF SUMMARY OF THE INVENTION

According to a first aspect of the invention, there is provided a torqueconverter including an impeller having a rotational axis and includingan impeller shell having a first engagement surface, and aturbine-piston coaxially aligned with and hydro-dynamically drivable bythe impeller. The turbine-piston includes a turbine-piston shell havinga turbine-piston flange with a first surface and an opposite secondengagement surface facing the first engagement surface of the impellershell. The turbine-piston is movable axially toward and away from thefirst engagement surface to position the torque converter respectivelyinto and out of a lockup mode in which the turbine-piston flange ismechanically locked to so as to be non-rotatable relative to theimpeller shell. The torque converter further includes an annular lockupresistance member including an annular elastomeric sandwich washercoaxially aligned with the rotational axis and disposed between theimpeller shell and the turbine-piston shell so as to resist axialmovement of the turbine-piston flange toward the first engagementsurface and into lockup with the impeller shell. The annular elastomericsandwich washer includes axially opposite first and second outermembers, and an elastomeric inner member sandwiched between the firstouter member and the second outer member.

According to a second aspect of the invention, there is provided ahydrokinetic torque coupling device for coupling together a drivingshaft and a driven shaft. The hydrokinetic torque coupling device ofthis second aspect includes a casing and a torque converter coaxiallyaligned with one another and rotatable about a rotational axis. Thecasing has a first engagement surface and includes an impeller shell anda casing shell interconnected to and non-rotatable relative to theimpeller shell. The torque converter includes an impeller having theimpeller shell, and a turbine-piston hydrodynamically drivable by theimpeller and including a turbine-piston shell. The turbine-piston shellincludes a turbine-piston flange having a second engagement surfacefacing the first engagement surface of the casing. The turbine-piston ismovable axially to move the second engagement surface toward and awayfrom the first engagement surface to position the hydrokinetic torquecoupling device respectively into and out of a lockup mode in which theturbine-piston flange is mechanically locked to so as to benon-rotatable relative to the casing. The torque converter furtherincludes an annular lockup resistance member including an annularelastomeric sandwich washer coaxially aligned with the rotational axisand disposed between the impeller shell and the turbine-piston shell soas to resist axial movement of the turbine-piston flange toward thefirst engagement surface and into lockup with the impeller shell. Theannular elastomeric sandwich washer includes axially opposite first andsecond outer members, and an elastomeric inner member sandwiched betweenthe first outer member and the second outer member.

A third aspect of the invention provides a method of assembling thehydrokinetic torque coupling device for coupling a driving shaft and adriven shaft together. The method involves providing a torque converterrotatable about a rotational axis. The torque converter comprises animpeller including an impeller shell having a first engagement surface,and a turbine-piston hydrodynamically drivable by the impeller andincluding a turbine-piston shell. The turbine-piston shell includes aturbine-piston flange having a second engagement surface facing thefirst engagement surface of the impeller shell. The turbine-piston ismovable axially toward and away from the first engagement surface toposition the torque converter respectively into and out of a lockup modein which the turbine-piston is mechanically locked to so as to benon-rotatable relative to the impeller shell. The torque converterfurther includes an annular lockup resistance member including anannular elastomeric sandwich washer coaxially aligned with therotational axis and disposed between the impeller shell and theturbine-piston shell so as to resist axial movement of theturbine-piston flange toward the first engagement surface and intolockup with the impeller shell. The annular elastomeric sandwich washerincludes axially opposite first and second outer members, and anelastomeric inner member sandwiched between the first outer member andthe second outer member. A casing cover shell is operatively connectedto the impeller shell to form a casing that is rotatable about therotational axis.

Other aspects of the invention, including apparatus, devices, systems,coupling devices, converters, processes, and the like which constitutepart of the invention, will become more apparent upon reading thefollowing detailed description of the exemplary embodiments.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING(S)

The accompanying drawings are incorporated in and constitute a part ofthe specification. The drawings, together with the general descriptiongiven above and the detailed description of the exemplary embodimentsand methods given below, serve to explain the principles of theinvention. The objects and advantages of the invention will becomeapparent from a study of the following specification when viewed inlight of the accompanying drawings, in which like elements are given thesame or analogous reference numerals and wherein:

FIG. 1 is a fragmented half-view in axial section of a hydrokinetictorque coupling device equipped with a turbine-piston in accordance witha first exemplary embodiment of the present invention;

FIG. 2 is an enlarged view of a fragment of the hydrokinetic torquecoupling device shown in the circle “II” in FIG. 1;

FIG. 3 is an enlarged view of a fragment of the hydrokinetic torquecoupling device shown in the circle “III” in FIG. 1;

FIG. 4 is a segmented perspective view of a lockup resistance member inaccordance with the first exemplary embodiment of the present invention;

FIG. 5 is a front view of the lockup resistance member in accordancewith the first exemplary embodiment of the present invention;

FIG. 6 is a side view of the lockup resistance member in accordance withthe first exemplary embodiment of the present invention;

FIG. 7 is a cross-sectional view of the lockup resistance member inaccordance with the first exemplary embodiment of the present invention;

FIG. 8 is a perspective view of a resilient member of the lockupresistance member in accordance with the first exemplary embodiment ofthe present invention;

FIG. 9 is a fragmented half-view in axial section of a hydrokinetictorque coupling device equipped with a turbine-piston in accordance witha second exemplary embodiment of the present invention;

FIG. 10 is an enlarged view of a fragment of the hydrokinetic torquecoupling device shown in the circle “X” in FIG. 9;

FIG. 11 is a cross-sectional view of the lockup resistance member inaccordance with the second exemplary embodiment of the presentinvention;

FIG. 12 is a simplified diagram of a hydrodynamic torque coupling deviceincluding a turbine-piston with a dual or double damper assembly;

FIG. 13 is a simplified diagram of another hydrodynamic torque couplingdevice including a turbine-piston with a single damper assembly;

FIG. 14 is a simplified diagram of still another hydrodynamic torquecoupling device including a turbine-piston with dual or double damperassemblies and a pendulum vibration absorber; and

FIG. 15 is a simplified diagram of a further hydrodynamic torquecoupling device including a turbine-piston with dual or double damperassemblies and a vibration absorbing spring-mass system.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENT(S) AND EMBODIED METHOD(S)OF THE INVENTION

Reference will now be made in detail to exemplary embodiments andmethods of the invention as illustrated in the accompanying drawings, inwhich like reference characters designate like or corresponding partsthroughout the drawings. It should be noted, however, that the inventionin its broader aspects is not limited to the specific details,representative devices and methods, and illustrative examples shown anddescribed in connection with the exemplary embodiments and methods.

This description of exemplary embodiments is intended to be read inconnection with the accompanying drawings, which are to be consideredpart of the entire written description. In the description, relativeterms such as “horizontal,” “vertical,” “up,” “down,” “upper,” “lower,”“right,” “left,” “top,” and “bottom” as well as derivatives thereof(e.g., “horizontally,” “downwardly,” “upwardly,” etc.) should beconstrued to refer to the orientation as then described or as shown inthe drawing figure under discussion. These relative terms are forconvenience of description and normally are not intended to require aparticular orientation. Terms concerning attachments, coupling and thelike, such as “connected” and “interconnected,” refer to a relationshipwherein structures are secured or attached to one another eitherdirectly or indirectly through intervening structures, as well as bothmovable or rigid attachments or relationships, unless expresslydescribed otherwise. The term “operatively connected” is such anattachment, coupling or connection that allows the pertinent structuresto operate as intended by virtue of that relationship. Additionally, thewords “a” and “an” as used in the claims means “at least one.”

A first exemplary embodiment of a hydrokinetic torque coupling device isgenerally represented in the accompanying drawings by reference numeral10, as best shown in the fragmentary sectional view in FIG. 1. Thehydrokinetic torque coupling device 10 is operable to fluidly ormechanically couple a driving shaft and a driven shaft of a motorvehicle, such as an automobile. In the typical case, the driving shaftis an output shaft of an internal combustion engine (not shown) of themotor vehicle and the driven shaft is connected to an automatictransmission of the motor vehicle.

The hydrokinetic torque coupling device 10 includes a sealed casing 12filled with a fluid, such as oil or transmission fluid. The sealedcasing 12, a hydrodynamic torque converter 14, and a torsional vibrationdamper (also referred to herein as a damper assembly) 16 are allrotatable about a rotational axis X. The drawings discussed herein showhalf-views, that is, the portion or fragment of the hydrokinetic torquecoupling device 10 above rotational axis X. Generally, the device 10 issymmetrical about the rotational axis X. Herein, the axial and radialorientations are considered with respect to the rotational axis X of thetorque coupling device 10. The relative terms such as “axially,”“radially,” and “circumferentially” are with respect to orientationsparallel to, perpendicular to, and around the rotational axis X,respectively.

The sealed casing 12 according to the first exemplary embodiment asillustrated in FIG. 1 includes a first casing shell (or casing covershell) 18 and a second casing shell 20 fixedly interconnected sealinglytogether, such as by welding at weld 19 at their outer peripheries, soas to be non-movable relative to one another. The first casing shell 18is fixedly interconnected to the driving shaft, more typically aflywheel (not shown) that is fixed to and non-rotatable relative to thedriving shaft, so that the casing 12 turns at the same speed that theengine operates for transmitting torque. Specifically, in theillustrated embodiment of FIG. 1 the casing 12 is rotatably driven bythe internal combustion engine and is non-rotatably coupled to theflywheel thereof with studs 21, shown in FIG. 1. Each of the first andsecond casing shells 18, 20 may be made, for example, formed integrallyby press-forming one-piece metal sheets.

The first casing shell 18 includes a first sidewall portion 22 extendingsubstantially radially relative to the direction from the rotationalaxis X (i.e., in a plane that is generally transverse to the rotationalaxis X) and a cylindrical first outer wall portion 26 ₁ extendingsubstantially axially from the first sidewall portion 22 toward thesecond casing shell 20. Similarly, the second casing shell 20 includes asecond sidewall portion 24 extending substantially radially relative tothe direction from the rotational axis X and a cylindrical second outerwall portion 26 ₂ extending substantially axially from the secondsidewall portion 24 toward the first casing shell 18. The secondsidewall portion 24 has a first engagement surface 25, best shown inFIG. 2. The first and second outer wall portions 26 ₁, 26 ₂ collectivelyestablish an annular outer wall 26 substantially parallel with therotation axis X. The weld 19 fixedly secures the outer wall portions 26₁ and 26 ₂ together.

The torque converter 14 includes an impeller (sometimes referred to asthe pump or impeller wheel) 30, a turbine-piston 32, and a stator(sometimes referred to as the reactor) 34 interposed axially between theimpeller 30 and the turbine-piston 32. The impeller 30, theturbine-piston 32, and the stator 34 are coaxially aligned with oneanother on the rotational axis X. The impeller 30, the turbine-piston32, and the stator 34 collectively form a torus. The impeller 30 and theturbine-piston 32 may be fluidly (or hydrodynamically) coupled to oneanother as known in the art.

The second casing shell 20 of the casing 12 also forms and serves as theimpeller shell of the impeller 30. Accordingly, the impeller shell 20sometimes is referred to as part of the casing 12. The impeller 30further includes a core ring 45, and a plurality of impeller blades 31fixedly attached, such as by brazing, to the impeller shell 20. Theimpeller 30, including the impeller shell 20, the core ring 45, and theblades 31, is fixedly secured to so as to be non-rotatable relative tothe first casing shell 18 and hence to the drive shaft (or flywheel) ofthe engine so that the impeller 30 rotates at the same speed as theengine output. The impeller 30 also includes an impeller hub 31 fixedlysecured to the impeller shell 20. The impeller hub 31 is arranged forengagement with a hydraulic pump of the transmission.

The hydrokinetic torque coupling device 10 further includes an outputhub 40 that is rotatable about the rotational axis X. The output hub 40is operatively coupled to and coaxial with the driven shaft. Forexample, the output hub 40 may be provided with internal splines 42 fornon-rotatably coupling the output hub 40 to the driven shaft, such as atransmission input shaft, provided with complementary external splines.Alternatively, a weld or other connection may be used to fix the outputhub 40 to the driven shaft. A radially outer surface of the output hub40 includes an annular slot 43 for receiving a sealing member, such asan O-ring 44. A sealing member 98, mounted to a radially innerperipheral surface of the output hub 40, creates a seal at the interfaceof the transmission input shaft and the output hub 40, as best shown inFIG. 1.

The turbine-piston 32 is a consolidation or incorporation of a turbinewith a lockup clutch piston. The turbine component of the turbine-piston32 includes a turbine-piston shell 35, a core ring 46, and a pluralityof turbine-piston blades 36 fixedly attached, such as by brazing, to theturbine-piston shell 35. The spinning of the impeller 30 causestransmission fluid in the torus to spin the turbine-piston blades 36,and hence the turbine-piston shell 35. The impeller shell 20 and theturbine-piston shell 35 collectively define a substantially toroidalfirst chamber (or torus chamber) 52 therebetween. Referring to FIG. 1,the torus chamber 52 is to the left side of the turbine-piston shell 35,and a second (or damper) chamber 54 is to the other (right) side of theturbine-piston shell 35. In other words, the first chamber 52 is definedbetween the impeller shell 20 and the turbine-piston shell 35, while thesecond chamber 54 is defined between the turbine-piston shell 35 and thefirst casing shell 18.

Returning to FIG. 1, the stator 34 is positioned between the impeller 30and the turbine-piston 32 to redirect fluid from the turbine-piston 32back to the impeller 30 in an efficient manner. The stator 34 istypically mounted on a one-way clutch 72 to prevent the stator 34 fromcounter-rotation. A thrust bearing 74 is interposed between a sidebearing ring 73, which is mounted to a side of the stator 34, and theimpeller shell 20 of the casing 12.

Extending axially at a radially inner peripheral end of theturbine-piston shell 35 is a substantially cylindrical flange 37 that isproximate to the rotational axis. The substantially cylindrical flange37 of the turbine-piston 32 is rotatable relative to the output hub 40.The sealing member (e.g., O-ring) 44 creates a seal at the interface ofthe substantially cylindrical flange 37 and the output hub 40. Asdiscussed in further detail below, the turbine-piston 32 is axiallymovably relative to the output hub 40 along this interface.

The piston component of the turbine-piston 32 includes a substantiallyannular, planar (i.e., flat) turbine-piston flange (or turbine-pistonwall) 38. The turbine-piston flange 38 is distal to the rotational axisX relative to the above-discussed proximal flange 37. The turbine-pistonflange 38 is a radial extension of the turbine-piston shell 35 and, asillustrated in FIG. 1, is disposed radially outside of theturbine-piston blades 36. The turbine-piston flange 38 and theturbine-piston shell 35 are embodied as integral with one another, e.g.,made of a single or unitary component, but may be separate componentsconnected together. The turbine-piston flange 38 extends from a radiallyouter peripheral end of the turbine-piston shell 35 radially outward,transverse to rotational axis X, to terminate at an end in spacedrelationship to the inner peripheral surface of the annular outer wallportion 26 of the casing 12. The turbine-piston flange 38 extendssufficiently outward radially to axially overlap with the secondsidewall portion 24 of the second casing shell 20.

As best shown in FIG. 2, the turbine-piston flange 38 has two axiallyopposite planar surfaces: a first flange surface 39 ₁ facing the firstsidewall portion 22 of the first casing shell 18, and an opposite secondengagement surface 39 ₂ facing the first engagement surface 25 of thesecond sidewall portion 24 of the second casing shell 20. The firstengagement surface 25 and the second engagement surface 39 ₂ areparallel to and face one another, and extend radially at a 90 degreeangle relative to the rotational axis X. The turbine piston 32 isaxially displaceable to move the second engagement surface 39 ₂ axiallytoward and away from the first engagement surface 25 of the casing 12 toposition the turbine-piston flange 38 of the turbine-piston 32respectively into and out of a lockup position, or, in other words, toposition the torque coupling device 10 into and out of a lockup mode,respectively. The second engagement surface 39 ₂ of the turbine-pistonflange 38 of the turbine-piston 32 and the first engagement surface 25of the second sidewall portion 24 of the casing 12 together create alockup clutch 50 that bypasses the hydrodynamic fluid coupling of thetorque converter 14 and mechanically couples the driving and drivenshafts.

In accordance with the first exemplary embodiment, the second engagementsurface 39 ₂ of the turbine-piston flange 38 is provided with a frictionring (or friction lining) 48, best shown in FIG. 2, which shows thelockup clutch 50 in a non-lockup mode. The friction ring 48 may besecured to the second engagement surface 39 ₂, for example, by adhesivebonding and/or with fasteners. The friction ring 48 is made of afriction material for improved frictional performance. Alternatively, afriction ring (or friction lining) may be secured to the firstengagement surface 25. According to still another embodiment, a firstfriction ring or liner is secured to the first engagement surface 25 ofthe casing 12 and a second friction ring or liner is secured to thesecond engagement surface 39 ₂. It is within the scope of the inventionto omit one or both of the friction rings.

Depending on conditions, when the torque converter 14 transmits torquehydro-dynamically, the action of the transmission fluid generates anaxial force which moves the turbine-piston 32 toward the impeller 30 andinto the lockup mode. This axial force varies depending on the speed,torque, drive, and coast. Under some stable or transient conditions, theaxial force may axially displace the turbine-piston 32 into contact withthe impeller 30 and close the lockup clutch 50 in unexpectedcircumstances, i.e., when hydrodynamic transmission mode is desired.Therefore, the chance of premature lock-up clutch engagement ispossible.

During the non-lockup mode of operation, when the torque converter 14transmits the movement hydro-dynamically (i.e., a hydrodynamictransmission mode of operation), the turbine-piston 32 is urged towardsthe stator 34, therefore the chance of pre-mature lock-up clutchengagement is possible. Instances of unintentional lockup can be reducedby including and/or increasing the biasing force of a spring locatedbetween the stator 34 and the turbine-piston shell 35. However, anincrease in spring biasing force can also slow the lockup response timeof the turbine-piston 32, and thereby increase the pressure necessary toaxially displace the turbine-piston 32 into lockup mode.

In order to avoid or at least reduce the occurrence ofunintended/premature lockup clutch engagement, the torque couplingdevice 10 further includes an annular lockup resistance member 80 in theform of an annular elastomeric sandwich washer. The annular elastomericsandwich washer 80 especially resists unintended lockup at lower speedratios by limiting displacement between the stator 34 and theturbine-piston 32 while the torque converter 14 is in the hydrodynamictransmission mode of operation. The elastomeric sandwich washer 80 isconfigured to urge the turbine-piston 32 axially away from the stator 34and is rotatable relative to at least one of the turbine-piston 32 andthe stator 34.

According to the embodiment shown in FIGS. 1, 6 and 7, the elastomericsandwich washer 80 is coaxially aligned with the rotational axis X andincludes a rigid (or stiff) non-elastomeric turbine-side (or first)outer member (or retainer) 82, a rigid (or stiff) non-elastomericstator-side (or second) outer member (or retainer) 84, and anelastomeric inner member 86 disposed (or sandwiched) between theturbine-side outer member 82 and the stator-side outer member 84. Theelastomeric sandwich washer 80 has two flat (or planar), axiallyopposite exterior surfaces: a turbine-side exterior surface 80 a and astator-side exterior surface 80 b.

As best shown in FIGS. 1 and 3, the turbine-side outer member 82 isadjacent (or juxtaposed) to and rotatable relative to the turbine-piston32, in particular the turbine-piston shell 35 of the turbine-piston 32,while the stator-side outer member 84 is adjacent to (or juxtaposed) androtatable relative to an annular retainer plate 75 of the stator 34. Forthis reason, the axially opposite exterior surfaces 80 a and 80 b of theelastomeric sandwich washer 80, which are in rotationally slidingcontact with an axially inner peripheral surface 33 the turbine-pistonshell 35 and an axial peripheral surface 75 a of the annular retainerplate 75 of the stator 34, respectively (as best shown in FIG. 3), maybe covered with anti-friction material such to account for differencesin rotational speed between the turbine-piston 32 and the stator 34. Inother words, the anti-friction material may be situated at the interfaceof the elastomeric sandwich washer 80 and the outer member(s) 82 and/or84. Alternatively, one of the axially opposite exterior surfaces 80 aand 80 b of the elastomeric sandwich washer 80 may be fixed to theturbine-piston shell 35 or the retainer plate 75 of the stator 34.

The elastomeric inner member 86 may be made from a variety of solidelastomeric materials, including rubber, polymer, foam, composites andany combination thereof. The elastomeric inner member 86 is secured toso as to be non-rotatable relative to both the turbine-side outer member82 and the stator-side outer member 84, such as by adhesive bonding. Asbest shown in FIG. 7, the elastomeric inner member 86 occupies theentire space between the turbine-side outer member 82 and thestator-side outer member 84. Each of the rigid turbine-side andstator-side outer members 82, 84 may be made of, for example, a rigid(or stiff) molded plastic and/or stamped metal. For example, theturbine-side outer member 82 may be made of stamped metal, while thestator-side outer member 84 is made of molded plastic, or vice versa.

As best shown in FIGS. 4 and 7, the turbine-side outer member 82 is inthe form of a ring having flat (or planar) axially opposite surfaces,one of which defines the turbine-side exterior surface 80 a of theelastomeric sandwich washer 80, while the other surface is adjacent andadhesively bonded to the elastomeric inner member 86.

The stator-side outer member 84 is generally circular in the radialdirection and has a flat (or planar) axially outer surface, whichdefines the stator-side exterior surface 80 b of the elastomericsandwich washer 80. The stator-side outer member 84 has one, two, three,or more, preferably two as best shown in FIG. 7, annular raised sections85 ₁ and 85 ₂ axially extending toward the turbine-side outer member 82.The annular raised sections 85 ₁ and 85 ₂, which are shown concentricwith one another, may be of the same or variable axial height. An innersurface of the stator-side outer member 84 located axially opposite tothe stator-side exterior surface 80 b is adhesively bonded to theelastomeric inner member 86.

The elastomeric inner member 86 is generally circular and has one, two,three, or more, preferably three as best shown in FIG. 7, annular raisedsections 88 ₁, 88 ₂ and 88 ₃ concentric with one another and axiallyextending between the turbine-side and the stator-side outer members 82and 84, as best shown in FIGS. 7 and 8. The annular raised sections 88₁, 88 ₂ and 88 ₃ may be of the same or variable axial height. As furtherillustrated in FIG. 7, the annular raised sections 85 ₁ and 85 ₂ of thestator-side outer member 84 are alternatingly disposed between theannular raised sections 88 ₁, 88 ₂ and 88 ₃ of the elastomeric innermember 86. In other words, each of the annular raised sections 88 ₁, 88₂ and 88 ₃ of the elastomeric inner member 86 is disposed radiallyadjacent to at least one of the annular raised sections 85 ₁ and 85 ₂ ofthe stator-side outer member 84.

The turbine-side outer member 82 and the stator-side outer member 84 arecoaxial to each other and axially spaced from each other by the width ofthe elastomeric inner member 86. Moreover, the turbine-side outer member82 and the stator-side outer member 84 are axially moveable relative toeach other due to the elasticity of the elastomeric inner member 86disposed therebetween.

However, in certain embodiments, a width of the lockup resistance member80 is selected such that the elastomeric sandwich washer 80 is notcompressed when no axial thrust force is applied to the turbine-piston32 in the direction toward the impeller 30, i.e., when no axial thrustforce is generated in the hydrodynamic transmission mode of operation.As a result, the lockup resistance member 80 does not bias (or urge) theturbine-piston 32 away from the impeller 30 when no axial thrust forceis generated in the hydrodynamic transmission mode of operation.

In the lockup mode, the first engagement surface 25 and the secondengagement surface 39 ₂ (or friction ring(s) 48 secured thereto) arepressed together such that the turbine-piston flange 38 of theturbine-piston 32 is frictionally non-rotatably coupled to the secondsidewall portion 24 of the casing 12, thereby mechanically locking theturbine-piston 32 to the casing 12. When not in the lockup mode, thefirst engagement surface 25 and the second engagement surface 39 ₂ arespaced from one another, such that the turbine-piston flange 38 is notfrictionally non-rotatably coupled to the casing 12. In the non-lockupmode, normal operation of the torque converter 14 hydrodynamicallycouples and decouples the impeller 30 to and from the turbine-piston 32.

The torsional vibration damper 16 is housed in the casing 12 axiallybetween the turbine-piston 32 and the first sidewall portion 22 of thecasing 12, as shown in FIG. 1. The torsional vibration damper 16 isconnected to a drive (or input) member 56 (discussed below), andincludes a plurality of first (or radially outer) circumferentialelastic damping members 60, an intermediate member 58 drivenly coupledto the drive member 56 through the first circumferential damping members60, a plurality of second (or radially inner) circumferential elasticdamping members 64, and a driven (or output) member 62 drivenly coupledto the intermediate member 58 through the second circumferential dampingmembers 64. The first circumferential damping members 60 are radiallyoutward from the second circumferential damping members 64. According tothe exemplary embodiment of FIG. 1, the first and second damping members60, 64 are configured as helical (or coil) springs orientedsubstantially circumferentially. Other elastic members may be selectedto replace or supplement the springs.

The drive member 56 is fixedly connected to the turbine-piston shell 35of the turbine-piston 32, such as by weld 55. The output side of thedrive member 56 has a plurality of driving tabs 57 (FIG. 1) extendingaxially in the direction away from the turbine-piston 32. The drivingtabs 57 of the drive member 56 are circumferentially equidistantlyspaced from one another, and engage circumferential ends of the firstdamping members 60.

The intermediate member 58 has a plurality of driven tabs 59 extendingaxially in an opposite direction to the driving tabs 57 of the drivemember 56. The driven tabs 59 of the intermediate member 58 arecircumferentially equidistantly spaced from one another, and engage theopposite circumferential ends of the first damping members 60 than thedriving tabs 57. The intermediate member 58 of the damper assembly 16 isrotatable relative to the drive member 56 and its driving tabs 57 due toelasticity of the first damping members 60, which absorb torsionalvibration.

Additionally, the driving tabs 57 of the drive member 56 are axiallymovable relative to the driven tabs 59 of the intermediate member 58.This relative axial movement between the driving tabs 57 and the driventabs 59 may become necessary during axial movement of the turbine-pistonshell 35 between its lockup and non-lockup modes. As discussed ingreater detail below, when the turbine-piston shell 35 shifts axiallydue to a lockup event, the driving tabs 57 move axially relative to thedriven tabs 59. Thus, the drive member 56 is both axially andcircumferentially moveable relative to the intermediate member 58, andgenerally to the damping assembly 16.

The radially inner portion of the intermediate member 58 forms or isconnected to a first disk part 68 on a first side of the second dampingmembers 64. The first disk part 68 is non-moveably secured to a seconddisk part 69 on the opposite side of the second damping members 64, suchas by rivets or welding. The first and second disk parts 68, 69establish an input part to the second damping members 64.

The driven member 62 establishes an output part of the second dampingmembers 64. The driven member 62 has windows in which the second dampingmembers 64 are set. The disk parts 68, 69 engage first ends of thesecond damping members 64, and the driven member 62 engages second endsof the second damping members 64. The disk parts 68, 69 are thusrotatable relative to the driven member 62, with the second dampingmembers 64 absorbing torsional vibration due to their elasticity.

The driven member 62 is non-rotatably connected, e.g., fixed, to theoutput hub 40. The non-rotatable connection between the driven member 62and the output hub 40 may be formed by splines or welding.Alternatively, the output hub 40 and the driven member 62 may beintegrally formed as a single piece. A thrust bearing 76 is positionedbetween the output hub 40 and the first casing shell 18.

As discussed above, the turbine-piston 32 is axially movable toward andaway from the impeller shell 20 between a lockup position and anon-lockup (open) position. Axial movement of the turbine-piston 32 isaccomplished by changing the pressure differential between the oppositesides of the turbine-piston shell 35, taking into account an elasticforce of the annular lockup resistance member 80. A pressure increase inthe damper chamber 54 relative to the torus chamber 52 (or stateddifferently a pressure decrease in the torus chamber 52 relative to thedamper chamber 54) that is greater than the stiffness of the annularlockup resistance member 80 shifts the turbine-piston shell 35 axiallyin the direction of torque transmission, i.e., towards the output sideof the casing 12, that is right to left in FIG. 1, into the lockup mode.On the other hand, a pressure decrease in the damper chamber 54 relativeto the torus chamber 52 (or stated differently a pressure increase inthe torus chamber 52 relative to the damper chamber 54) acts with theelastic force of the elastomeric inner member 86 of the elastomericsandwich washer 80 to shift the turbine-piston shell 35 and theturbine-piston flange 38 axially against the direction of torquetransmission, i.e., towards the input side of the casing, that is leftto right in FIG. 1, out of the lockup mode. Pressure changes are createdby control of the fluid, e.g., hydraulic fluid or oil, in the chambers52 and 54.

In the lockup mode, the turbine-piston shell 35 is displaced axiallytowards the impeller 30 until the frictional ring 48 of the secondengagement surface 39 ₂ of the turbine-piston flange 38 (which movesaxially with the turbine-piston shell 35) abuts against and isnon-rotatably frictionally coupled to the first engagement surface 25 ofthe casing 12. In the lockup mode, torque is transferred from the engineto the casing 12, then by way of the frictional engagement betweensurfaces 25 and 39 ₂ (or the frictional lining 48 thereof) through theturbine piston shell 35 to the drive member 56 welded thereto, thenserially to the damping assembly 16 and the output hub 40.

As the turbine-piston 32 and the drive member 56 move axially into thelockup position as described above, the driving tabs 57 of the drivemember 56 are axially displaced relative to the driven tabs 59 of theintermediate member 58. The relative axial movement of the driving tabs57 relative to the driven tabs 59 allows the intermediate member 58, thedriven member 62, and the damping members 60, 64 to remain fixed axiallyon the output hub 40 while the turbine-piston 32 and the drive member 56move in the axial direction. Moreover, the friction ring 48 secured tothe second engagement surface 39 ₂ may have a plurality ofcircumferentially spaced grooves (not shown) extending generallyradially so as to fluidly connect the torus chamber 52 and the damperchamber 54 with one another in the lockup mode for cooling frictionsurfaces of the lockup clutch 50 by the working fluid and creating avery high pressure difference between the torus and damper chambers 52,54.

In the non-lockup mode, the turbine-piston 32 is displaced axially awayfrom the impeller 30, axially moving the turbine-piston shell 35 and theturbine-piston flange 38 until the second engagement surface 39 ₂ (orthe frictional lining 48 thereof) is spaced from and no longernon-rotatably frictionally coupled to the first engagement surface 25.Thus, torque is transferred from the engine to the casing 12 in ahydrodynamic transmission mode that does not bypass the torque converter14 through the lockup clutch 50. The driving tabs 57 move axiallytowards the driven tabs 59 as the lockup clutch 50 is moved from thelockup mode to the non-lockup mode. Notably, in the non-lockup mode anopen fluid passage is established between the first engagement surface25 of the casing 12 and the second engagement surface 39 ₂. Hydraulicfluid is free to flow between the torus chamber 52 and the damperchamber 54 through the passage.

In operation, the lockup clutch 50 is generally activated after thehydraulic hydrodynamic coupling of the driving and driven shafts,typically at relatively constant speeds, in order to avoid the loss ofefficiency caused in particular by slip phenomena between theturbine-piston 32 and the impeller 30. Because of the axial pressuresacting on the turbine-piston 32 for movement between its lockup andnon-lockup positions, the turbine-piston shell 35 may be made somewhatthicker than typical turbine shells that do not form or function as thelockup piston.

The turbine-piston 32 both forms the shell component of the turbine andthe piston component of the lockup clutch 50, as described above. Byconsolidating two components that are normally separate from one anotherinto a single component, space is saved in the hydrokinetic torquecoupling device 10. This space-saving structure provides several designoptions. For example, the hydrokinetic torque coupling device 10 can bemade smaller and lighter. Alternatively, the free space within thecasing 12 can be used to add more additional components, such as dampingcomponents.

Various modifications, changes, and alterations may be practiced withthe above-described embodiment, including but not limited to theadditional embodiment shown in FIGS. 9-11. In the interest of brevity,reference characters in FIGS. 9-11 that are discussed above inconnection with FIGS. 1-8 are not further elaborated upon below, exceptto the extent necessary or useful to explain the additional embodimentof FIGS. 9-11. Modified components and parts are indicated by theaddition of a hundred digits to the reference numerals of the componentsor parts.

In a hydrokinetic torque coupling device 110 of a second exemplaryembodiment illustrated in FIGS. 9-11, the torque converter 14 with theannular elastomeric sandwich washer 80 is replaced by a torque converter114 (FIG. 9) with an annular elastomeric sandwich washer 180. In thesecond exemplary embodiment of the present invention illustrated inFIGS. 9-11, the elastomeric sandwich washer 180 is coaxially alignedwith the rotational axis X and includes a rigid (or stiff)non-elastomeric turbine-side outer member (or retainer) 182, a rigid (orstiff) non-elastomeric stator-side outer member (or retainer) 184, andfirst and second elastomeric rings 186 ₁ and 186 ₂ disposed (orsandwiched) between the rigid turbine-side outer member 182 and therigid stator-side outer member 184. The elastomeric rings 186 ₁ and 186₂ are concentric to and radially spaced from each other, as best shownin FIG. 10. Although two elastomeric rings 186 ₁ and 186 ₂ are shown inthe illustrated embodiment of FIGS. 9-11, it should be understood thatthe elastomeric sandwich washer 180 may contain one, two, three, or moreconcentric rings.

As best shown in FIGS. 10 and 11, the elastomeric sandwich washer 180has two flat (or planar), axially opposite exterior surfaces: aturbine-side exterior surface 180 a and a stator-side exterior surface180 b. The turbine-side exterior surface 180 a is defined by the side ofthe turbine-side outer member 182 and is adjacent (or juxtaposed) to androtatable relative to the turbine-piston 32, in particular theturbine-piston shell 35 of the turbine-piston 32. The stator-sideexterior surface 180 b is defined by the stator-side outer member 184and is adjacent to (or juxtaposed) and rotatable relative to an annularretainer plate 75 of the stator 34. For this reason, the axiallyopposite exterior surfaces 180 a and 180 b of the elastomeric sandwichwasher 180, which are in circumferentially sliding contact with anaxially inner peripheral surface 33 the turbine-piston 32 and an axialperipheral surface 75 a of the annular retainer plate 75 of the stator34, respectively (as best shown in FIGS. 9 and 10), may be covered withanti-friction material such to account for differences in rotationalspeed between the turbine-piston 32 and the stator 34. In other words,the anti-friction material may be situated at the interface of theelastomeric sandwich washer 180 and the outer member(s) 182 and/or 184.Alternatively, one of the axially opposite exterior surfaces 180 a and180 b of the elastomeric sandwich washer 180 may be fixed to theturbine-piston shell 35 or the retainer plate 75 of the stator 34.

The elastomeric rings 186 ₁ and 186 ₂ may be made from a variety ofsolid elastomeric materials, including rubber, polymer, foam, compositesand any combination thereof. The elastomeric rings 186 ₁ and 186 ₂ arenon-rotatably attached to both the turbine-side outer member 182 and thestator-side outer member 184, such as by adhesive bonding. As best shownin FIG. 11, the elastomeric rings 186 ₁ and 186 ₂ occupy the spacebetween the turbine-side outer member 182 and the stator-side outermember 184 so as to define an axial clearance k between axially innerperipheral surfaces of the turbine-side and stator-side outer members182, 184. Each of the rigid turbine-side and stator-side outer members182, 184 may be made of, for example, a rigid (or stiff) molded plasticand/or stamped metal.

According the second exemplary embodiment the rigid turbine-side andstator-side outer members 182, 184 are structurally and dimensionallyidentical. As best shown in FIGS. 10 and 11, the turbine-side outermember 182 is in the form of an annular piece having completely flat (orplanar) axially outer surface, which defines the turbine-side exteriorsurface 180 a of the elastomeric sandwich washer 180, while an axiallyinner surface of the turbine-side outer member 182 is adjacent to theelastomeric rings 186 ₁ and 186 ₂ and is adhesively bonded thereto.

The stator-side outer member 184 is generally annular in the radialdirection and has a flat (or planar) axially outer surface, whichdefines the stator-side exterior surface 180 b of the elastomericsandwich washer 180. An axially inner surface of the stator-side outermember 184 is adjacent to the elastomeric rings 186 ₁ and 186 ₂ and isadhesively bonded thereto.

Each of the turbine-side and stator-side outer members 182, 184 has tworadially spaced, annular and coaxial first grooves 182 ₁, 182 ₂ andsecond grooves 184 ₁, 184 ₂ receiving the first and second elastomericrings 186 ₁ and 186 ₂ therebetween, respectively. As best shown in FIG.11, the first elastomeric ring 186 ₁ occupies the space between thefirst grooves 182 ₁, 18 ₄₁ of the rigid turbine-side and stator-sideouter members 182, 184, while the second elastomeric ring 186 ₂ occupiesthe space between the second grooves 182 ₂, 184 ₂ of the rigidturbine-side and stator-side outer members 182, 184. Moreover, theelastomeric rings 186 ₁ and 186 ₂ occupy the space between theturbine-side outer member 182 and the stator-side outer member 184 so asto define an axial clearance k between axially inner peripheral surfacesof the turbine-side and stator-side outer members 182, 184.

The turbine-side outer member 182 and the stator-side outer member 184are concentric to each other and axially spaced from each other.Moreover, the turbine-side outer member 182 and the stator-side outermember 184 are axially moveable relative to each other due to theelasticity of the elastomeric rings 186 ₁ and 186 ₂ disposedtherebetween.

The sliding engagement by the axially opposite exterior surfaces 180 aand 180 b of the elastomeric sandwich washer 180 relative to the stator34 and the turbine-piston 32 allows the annular lockup resistance member180 to rotate relative to the stator 34 and the turbine-piston 32 whenthe lockup clutch 50 of the torque coupling device 110 is in non-lockupmode. Anti-friction material may be situated at the interface of theelastomeric sandwich washer 180 and the stator 34 and/or theturbine-piston 32. The purpose of the annular lockup resistance member180 is to resist the axial thrust load generated by hydrodynamictransmission during the non-lockup mode, thus keeping the lockup clutch50 disengaged until proper speed ratio between the turbine-piston 32 andthe impeller 30 is achieved. However, the annular lockup resistancemember 180 may be adapted not to bias (or urge) the turbine-piston 32away from the impeller 30 when no axial thrust force is generated duringthe operation of the torque coupling device which is applied to theturbine-piston 32 in the direction toward the impeller 30.

Other variations and modifications of the annular lockup resistancemember 80 may be practiced with the present invention. The features ofthe above-described embodiments may be practiced with one another andare substitutable in numerous combinations.

An exemplary method for assembling the hydrokinetic torque couplingdevice 10 according to the embodiment of FIGS. 1-8 will now beexplained. It should be understood that this exemplary method may bepracticed in connection with the other embodiments described herein.This exemplary method is not the exclusive method for assembling thehydrokinetic torque coupling devices described herein.

The impeller 30, the turbine-piston 32, the stator 34, the annularlockup resistance member 80/180, and the damper assembly 16 may each bepreassembled. The turbine-piston 32 includes, as noted above, theturbine-piston shell 35 the turbine-piston blades 36 attached to theturbine-piston shell 35, and the turbine-piston flange 38.

The impeller 30, the stator 34, the lockup resistance member 80/180, andthe turbine-piston 32 subassemblies are assembled together as shown inthe drawings. The cylindrical flange 37 of the turbine-piston 32 ismounted to slidingly engage the hub 40 (splined with or mounted on thedriven shaft at 42) with the seal 44 therebetween. The damper assembly16 is then added. The driving tabs 57 are engaged with the damperassembly 16, and the driven member 62 is engaged to the output hub 40,as described above. The first casing shell 18 is non-moveably andsealingly secured, such as by welding at 19, to the second casing shell20, as best shown in FIG. 1. The hydrokinetic torque coupling device 110of FIGS. 9-11 can be assembled in a similar manner.

The torque converters and hydrodynamic torque coupling devices describedherein may incorporate different damper assemblies. For example, FIG. 12shows a hydrodynamic torque coupling device including the impeller 30and the turbine-piston 32 for establishing the hydrodynamic transmissionmode and the lockup clutch 50 for lockup mode transmission. The impeller30/turbine-piston 32 combination and the lockup clutch 50 are arrangedparallel to one another and serially between the casing 12 and theturbine-piston shell 35. The elastic damping members 60 and 64 of thedamper assembly 16 and the output hub 40 are arranged seriallydownstream of the turbine-piston shell 35 in FIG. 12. The diagram ofFIG. 12 generally corresponds to the arrangement of the embodimentsshown in FIGS. 1 and 9.

FIG. 13 shows an alternative damper assembly 116 similar to that of FIG.12, but in which the damper assembly 16 is modified to include only oneset of circumferentially extending elastic damping members 60.

A damper assembly 216 shown in FIG. 14 is similar to that of FIG. 12,but further includes a centrifugal pendulum oscillator 96 coupled to theintermediate member 58. Centrifugal pendulum oscillators (or pendulumvibration absorbers) are well known in the art and described in, forexample, U.S. patent application Ser. No. 14/305,128 filed Jun. 16,2014, GB598811 to Stone, U.S. Pat. No. 6,026,940 to Sudau, and EP1744074to Grahl. The centrifugal pendulum oscillator 96 may be coupled to thecircumference of the intermediate member 58 and may be arranged on bothsides of the intermediate member 58.

A damper assembly 316 shown in FIG. 15 is similar to that of FIG. 12,but further includes a spring mass system 99 coupled to the intermediatemember 58. Spring-mass systems are well known in the art and describedin, for example, WO 2004/018897 to Haller. The spring-mass system 99 maybe coupled to the circumference of the intermediate member 58. Thespring of the spring-mass system 99 may be a coil spring, such as asteel spring. The damper may be any linear or non-linear damper,including for example a viscous damper. The spring and mass may beembodied as two components or one integral component. The spring-masssystem may have a linear or non-linear constant or variable stiffness,and a constant or variable mass.

The features of the above-described embodiments are substitutable innumerous combinations.

The foregoing description of the exemplary embodiment(s) of the presentinvention has been presented for the purpose of illustration inaccordance with the provisions of the Patent Statutes. It is notintended to be exhaustive or to limit the invention to the precise formsdisclosed. The embodiments disclosed hereinabove were chosen in order tobest illustrate the principles of the present invention and itspractical application to thereby enable those of ordinary skill in theart to best utilize the invention in various embodiments and withvarious modifications as suited to the particular use contemplated, aslong as the principles described herein are followed. This applicationis therefore intended to cover any variations, uses, or adaptations ofthe invention using its general principles. Further, this application isintended to cover such departures from the present disclosure as comewithin known or customary practice in the art to which this inventionpertains. Thus, changes can be made in the above-described inventionwithout departing from the intent and scope thereof. It is also intendedthat the scope of the present invention be defined by the claimsappended thereto.

What is claimed is:
 1. A hydrodynamic torque converter comprising: animpeller having a rotational axis and comprising an impeller shellhaving a first engagement surface; a turbine-piston coaxially alignedwith and hydrodynamically drivable by the impeller, the turbine-pistoncomprising a turbine-piston shell comprising a turbine-piston flangehaving a second engagement surface facing the first engagement surfaceof the impeller shell, the turbine-piston being movable axially towardand away from the first engagement surface to position the torqueconverter respectively into and out of a lockup mode in which theturbine-piston is mechanically locked to so as to be non-rotatablerelative to the impeller shell; an annular lockup resistance membercomprising an annular elastomeric sandwich washer coaxially aligned withthe rotational axis and disposed between the impeller shell and theturbine-piston shell so as to resist axial movement of theturbine-piston toward the first engagement surface and into the lockupmode, the annular elastomeric sandwich washer comprising axiallyopposite first and second outer members; and an elastomeric inner membersandwiched between the first outer member and the second outer member.2. The torque converter of claim 1, wherein the elastomeric inner memberis attached directly to both the first outer member and the second outermember.
 3. The torque converter of claim 2, wherein the first outermember and the second outer member are axially spaced from each otherand axially moveable relative to each other due to the elasticity of theelastomeric inner member disposed therebetween.
 4. The torque converterof claim 3, wherein the elastomeric inner member is generally circularand has at least one annular raised section axially extending betweenthe first outer and the second outer members.
 5. The torque converter ofclaim 4, wherein the second outer member has at least one annular raisedsection axially extending toward the first outer member; and wherein theat least one annular raised section of the elastomeric inner member isdisposed radially adjacent to the at least one annular raised section ofthe second outer member.
 6. The torque converter of claim 3, wherein theelastomeric inner member includes two elastomeric rings coaxial to eachother and radially spaced from each other.
 7. The torque converter ofclaim 1, further comprising a stator situated between the impeller andthe turbine-piston; wherein the elastomeric sandwich washer is situatedbetween the stator and the turbine-piston shell so that the first outermember is adjacent to the turbine-piston shell of the turbine-piston andthe second outer member is adjacent to the stator.
 8. The torqueconverter of claim 7, wherein the elastomeric sandwich washer isrotatable relative to at least one of the turbine-piston and the stator.9. The torque converter of claim 8, wherein the elastomeric sandwichwasher has a planar turbine-side exterior surface that circumferentiallyslidingly engages and is rotatable relative to the turbine-piston whenthe torque converter is out of the lockup mode.
 10. The torque converterof claim 7, wherein the elastomeric sandwich washer has a planarstator-side exterior that circumferentially slidingly engages and isrotatable relative to the stator when the torque converter is out of thelockup mode.
 11. The torque converter of claim 1, further comprising afriction lining secured to the first engagement surface of the impellershell or the second engagement surface of the turbine-piston flange. 12.A hydrokinetic torque coupling device for coupling together a drivingshaft and a driven shaft, the hydrokinetic torque coupling device beingrotatable about a rotational axis and comprising: a casing comprising animpeller shell and a casing shell interconnected to and non-rotatablerelative to the impeller shell, the casing being rotatable about therotational axis and having a first engagement surface; and a torqueconverter coaxially aligned with and rotatable about the rotationalaxis, the torque converter comprising: an impeller comprising theimpeller shell; a turbine-piston hydrodynamically drivable by theimpeller and comprising a turbine-piston shell, the turbine-piston shellcomprising a turbine-piston flange having a second engagement surfacefacing the first engagement surface of the casing, the turbine-pistonbeing movable axially toward and away from the first engagement surfaceto position the hydrokinetic torque coupling device respectively intoand out of a lockup mode in which the turbine-piston is mechanicallylocked to so as to be non-rotatable relative to the casing; and anannular lockup resistance member comprising an annular elastomericsandwich washer coaxially aligned with the rotational axis and disposedbetween the impeller shell and the turbine-piston shell so as to resistaxial movement of the turbine-piston toward the first engagement surfaceand into the lockup mode, the annular elastomeric sandwich washercomprising axially opposite first and second outer members; and anelastomeric inner member sandwiched between the first outer member andthe second outer member.
 13. The hydrokinetic torque coupling device ofclaim 12, further comprising a stator situated between the impeller andthe turbine-piston; wherein the elastomeric sandwich washer is situatedbetween the stator and the turbine-piston shell so that the first outermember is adjacent to the turbine-piston shell of the turbine-piston andthe second outer member is adjacent to the stator.
 14. The hydrokinetictorque coupling device of claim 13, further comprising: an output hub;and a torsional vibration damper interconnecting the turbine-piston andthe output hub.
 15. The hydrokinetic torque coupling device of claim 14,further comprising a drive member non-movably connected to theturbine-piston shell and connecting the turbine-piston shell to thetorsional vibration damper, the torsional vibration damper furthercomprising a driven member operatively coupled to the output hub, andwherein the drive member is axially movable relative to the drivenmember of the torsional vibration damper.
 16. The hydrokinetic torquecoupling device of claim 14, further comprising a drive memberinterconnecting the turbine-piston shell to the torsional vibrationdamper, wherein the torsional vibration damper comprises an intermediatemember, a first set of circumferentially extending elastic dampingmembers drivingly coupling the drive member to the intermediate member,a driven member connected to and non-rotatable relative to the outputhub, a second set of circumferentially extending elastic damping membersdrivingly coupling the intermediate member to the driven member, and acentrifugal pendulum oscillator mounted to the intermediate member. 17.The hydrokinetic torque coupling device of claim 14, further comprisinga drive member interconnecting the turbine-piston shell to the torsionalvibration damper, wherein the torsional vibration damper comprises anintermediate member, a first set of circumferentially extending elasticdamping members drivingly coupling the drive member to the intermediatemember, a driven member connected to and non-rotatable relative to theoutput hub, a second set of circumferentially extending elastic dampingmembers drivingly coupling the intermediate member to the driven member,and a spring mass system coupled to the intermediate member.
 18. Thehydrokinetic torque coupling device of claim 12, wherein theturbine-piston shell and the turbine-piston flange are axially movabletowards an output side of the hydrokinetic torque coupling device inorder to frictionally couple the first engagement surface and the secondengagement surface for positioning the turbine-piston in the lockupmode, and wherein the turbine-piston shell and the turbine-piston flangeare axially movable towards an input side of the hydrokinetic torquecoupling device so that the first engagement surface and the secondengagement surface are not frictionally coupled and the turbine-pistonis out of the lockup mode.
 19. The hydrokinetic torque coupling deviceof claim 13, wherein the first outer member and the second outer memberare axially spaced from each other and axially moveable relative to eachother due to the elasticity of the elastomeric inner member disposedtherebetween; and wherein the elastomeric sandwich washer is rotatablerelative to at least one of the turbine-piston and the stator.
 20. Amethod of assembling a hydrokinetic torque coupling device for couplinga driving shaft and a driven shaft together, comprising: providing atorque converter rotatable about a rotational axis, the torque convertercomprising: an impeller comprising the impeller shell, the impellershell having a first engagement surface; a turbine-pistonhydrodynamically drivable by the impeller and comprising aturbine-piston shell, the turbine-piston shell comprising aturbine-piston flange having a second engagement surface facing thefirst engagement surface of the impeller shell, the turbine-piston beingmovable axially toward and away from the first engagement surface toposition the torque converter respectively into and out of a lockup modein which the turbine-piston is mechanically locked to so as to benon-rotatable relative to the impeller shell; and an annular lockupresistance member comprising an annular elastomeric sandwich washercoaxially aligned with the rotational axis and disposed between theimpeller shell and the turbine-piston shell so as to resist axialmovement of the turbine-piston toward the first engagement surface andinto lockup with the casing, the annular elastomeric sandwich washercomprising axially opposite first and second outer members; and anelastomeric inner member sandwiched between the first outer member andthe second outer member; and operatively connecting a casing cover shellto the impeller shell of the torque converter to form a casing that isrotatable about the rotational axis.